Apparatus for forming one piece metallic can bodies

ABSTRACT

A horizontally movable ram is mounted on a main frame longitudinally reciprocal in a forward working stroke and a rearward return stroke through a rotating crankshaft drivingly connected to the ram by a plurality of pivot arms, the pivot arms being specifically arranged for longitudinally moving the ram at a reduced comparative speed directly approaching and following the ram stroke rearward reversal than directly approaching and following the ram stroke forward reversal permitting an increased period of time for feeding of metal parts to be engaged and worked by the ram. The ram is mounted on the main frame through hydrostatic-type pressurized oil film bearing assemblies with the ram being supported at a rearward location by combined horizontally extending and vertically extending constantly pressurized and flowing oil films with a more forward portion of the ram being additionally peripherally supported by a cylindrical constantly pressurized and flowing oil film. The apparatus die pack may include an initial redraw die and a series of ironing dies, each of said dies including a die ring resiliently retained for limited radial movement and also adjustment alignment, as well as arranged in the particular die for selective removal out of its particular die assembly by pivoting of a cover plate without complete removal of the die assembly from the die pack. Additionally, the ironing die assemblies each include a fluid distribution ring longitudinally adjacent the die ring thereof and preferably removable therewith as an assembly arranged to tangentially distribute a circumferentially moving ring of liquid across the distribution ring ram opening providing lubrication and cooling for the dies and metal parts being formed.

llnite States atent 1191 Paramonoff 1 May 29, 1973 APPARATUS FOR FORMINGONE ABSTRACT PIECE METALLIC CAN BODIES A horizontally movable ram ismounted on a main {75] Inventor: Elpidifor Paramonoff, Los Angeles,frame longitudinally reciprocal in a forward working C lif stroke and arearward return stroke through a rotating crankshaft drivingly connectedto the ram by a plurali- [731 Asslgnee: standun Compton Cahfty of pivotarms, the pivot arms being specifically ar- [22] Filed: June 11 1970ranged for longitudinally moving the ram at a reduced comparative speeddirectly approaching and following PP N05 ,430 the ram stroke rearwardreversal than directly approaching and following the ram stroke forwardreversal permitting an increased period of time for feeding (g1..72/349, 72/422,;30242]; of metal parts to be g g and worked y the ram.

. The ram is mounted on the main frame through of Search y yppressurized bearing assem 450; 308/5 R blies with the ram beingsupported at a rearward location by combined horizontally extending andvertically References Cited extending constantly pressurized and flowingoil films with a more forward portion of the ram being addi- UNITEDSTATES PATENTS tionally peripherally supported by a cylindrical con-3,663,072 5 1972 Cvacho ..308/5 R stantly pressurized and flowing Oilfilm. The apparatus 3,466,951 9/1969 Greenberg ..30s 5 R i p k y includen initial redraw die and a series 3,582,159 6/1971 Uhtenwoldt ..308/5 Rof ironing dies, each of said dies including a die ring 3,635,532 1/1972Zerbola resiliently retained for limited radial movement and 3,270,5449/1966 Maeder et al.. also adjustment alignment, as well as arranged-inthe 2,664,191 12/1953 May ..72/347 particular die for selective removalout of its particu- 3,030,744 4/1962 Mueller lar die assembly bypivoting of a cover plate WithOUt 3,127,955 4/1964 Macks ..308/5complete remgval of the die assembly from the die ack. Additionall theironing die assemblies each in- FOREGN PATENTS OR APPLICATIONS Elude afluid distiibution ring longitudinally adjacent 876,171 8/1961 GreatBritain ..308/5 the die ring thereof and Preferably removable 310,9351/1956 Switzerland ..308/5 therewith an assembl arranged Ian .entially702,5s4 1/1954 Great Britain ..308/5 mbme a crcumferemla y mvmg lqudacmss the distribution ring ram opening providing lubrication andcooling for the dies and metal parts being formed.

PATENIEWQQIQH 735529 sum 01 [1F 11 V INl liN'I' /k.

EL PIDIFOF? PARAMONOFF 4 BYMAHONEY HORNBA KER 4 AND SCH/0K A TTORNEYSPATgmmLtYzslm 7 5,5 9

sum 02 0F 11 FIG. 4.

INVENTOR. ELPlD/FOR PARAMONOF F "IVIAHONEY, HORNBAKER AND SCH/CK b J [mATTORNEYS PATENT'LL 3.735.629

sum 03 SF 11 FIG. 5.

IN VEN TOR. E L PIDIFOR PARA MONOFF MAHONEY, HORNBA KER AND SCH/CKATTORNEYS PATENIflH-HYZSIUYS 3 735,629

FIG. 2/.

I NVENTOR. ELP/DIFOR PARAMONOFF BYMAHONEY, HORNBAKER AND S CHICKATTORNEYS PATENT'LU B 32m US UP 11 IN VENTOR. ELPIDIFOR PARAMONOFFBYMAHONEY, HORNBAKER AND SCH/CK ATTORNEYS PATENTLO W 3,735,629

sum 11 0F11 L. J INVENTOR. ELPIDIFOR PARAMONOFF --*--1BYMAHONEY,HORNBAKER AND SCH/CK ATTORNEYS APPARATUS FOR FORMING ONE PmCEMETALLIC CAN BODIES BACKGROUND OF THE INVENTION This invention relatesto an apparatus for forming one piece metallic can bodies and moreparticularly, to such an apparatus which may include reciprocal ramacting through a die pack incorporating multiple ironing dies, andsometimes incorporating an initial redraw die, for forming one piecemetallic can bodies from previously formed cup-like metallic parts. Evenmore particularly, the principles of the present invention may includeany one or all in combination of a novel mechanical drive for thereciprocal ram arranged for high speed ram movement during a workingportion thereof and reduced speed ram movement during a part feedingportion thereof, hydrostatic-type bearing support for the reciprocal ramwherein the ram movements are supported on constantly pressurized andflowing, thickened oil films for maximum movement accuracy and minimumwear, and a novel arrangement of die pack assembly having improved diemounting providing sufficient die lubrication and cooling throughout theworking operation with convenient die accessibility for maintenancewithout disturbing the remainder of the die pack assembly.

Various prior forms of apparatus for forming one piece metallic canbodies have heretofore been provided, all of which have necessarilyrequired the use of a reciprocally movable ram movable through arelatively long forward working and rearward return stroke throughmultiple stages or ironing dies in order to in crease the axial orlongitudinal length of a cup shaped metal part in order to produce afinished metallic can body. Obviously, unless multiple ironing stagesare incorporated in a single apparatus, the various progres sive ironingstages must be accomplished singly, thus the requirement of theextensive ram stroke. To even further increase the problems involved,particularly where the starting cup-like metallic Parts to be ironedinto finished can bodies are formed of metals which are more difficultof drawing and ironing, it is sometimes desirable to include with themultiple ironing stages comprised of the multiple ironing dies, aninitial redraw stage to thereby even further increase the over-all diepack assembly length and the necessary reciprocal strokes of the ram.

Consequently, three major problem areas have been encountered in theconstruction of apparatus of the type herein involved. A first majorproblem area is the manner of drive of the reciprocal ram, that is,exactly how to reciprocally drive the ram over its extensive forwardworking and return stroke at maximum lineal speeds of predetermineduniformity while still permitting sufficient time during such rammovement for the feeding of cup-like metallic parts into a workingposition from which the various working oPerations can subsequentlyfollow. Another maJor problem area is exactly how to support the ramduring its reciprocal movements while still maintaining repeatedtrueness of movement with minimum wear for maximum quality of finishedcan bodies. Still another problem area is that of the die pack assemblywherein sufficient redraw and ironing die support must be maintainedwhile still incorporating proper die and metal part lubrication andcooling, all in a die pack assembly of a convenient form 1 permittingthe maximum ease of periodic maintenance inspections and replacements.

Two general types of ram drive have heretofor been incorporated invarious of the metallic can body forming mechanisms, hydraulic drive byhydraulic cylinder systems sometimes including mechanical drive elementstherewith and pure mechanical drive solely by a crankshaft and pivotalmechanical linkages. Both of these prior forms of drive have includedcertain advantages and certain disadvantages, keeping in mind that theover-all goal is maximum speed with a predeterminability of uniformityin movement matched against a sufficient allowable time element duringportions of the ram stroke during which the cup-like metallic parts tobe ironed or redrawn and ironed may be fed into the proper workingposition for engagement by the ram to carry out the working operations.

With the ram hydraulic drive, whether or not me chanical drive portionsare included therewith, it is possible, with relatively complicatedhydraulic controls, to gain relatively high ram speeds during theworking operations, while still reducing the ram speeds during theportions of the ram strokes wherein the cup-like metallic part feedingmust take place. Driving the ram hydraulically, however, results insufficiently varying uniformity of ram movement due to hydraulic fluidunavoidable temperature changes and leakage that the quality of thefinally produced metallic can bodies can vary over a considerable range.Thus, scrap losses can be extensive and particularly unless themechanism involved is maintained at peak maintenance preciseness andadjustment.

With the use of mechanical drives in such mechanisms for the reciprocalram movements, and considering purely the ram movements withoutintroducing the problems of part feeding, relatively high ram speeds canagain be obtained and, assuming proper ram movement guiding ismaintained by frequent bearing maintenance, constant uniformity of ramreciprocal movement for maximum finished can body quality can likewisebe obtained. Introducing the problem of timing for cup-like metallicpart initial feeding, however, serves to greatly reduce the possible ramspeed during both the feeding and working operations. That is, withmechanical ram drive in the previous can body forming mechanisms, theram speeds have been of substantially uniform cycle throughout each ofthe working and return strokes. As a result, the speed of the workingstroke is the same as the speed of the return stroke and the speed ofthe working operation is necessarily limited by the timing required foraccomplishing the feeding operation since with mechanical drive it hasheretofor been impossible to alter the ram cycling speeds during thefeeding operation from that produced during the working operation.

In the second major problem area, that of bearing support for the ramover the relatively long reciprocal strokes required for multiple stageironing operations, and even including the initial redrawing operation,during which the ram must be extended or projected within the dies overa long unsupported distance, the ram bearing support in the prior canbody forming mechanisms has been an operational speed limiting factor iffrequent failures and maintenance interruprions for bearing replacementsare to be avoided. Again, in the carrying out of multiple redraw andironing operations on one piece metallic can bodies with the thin metalwall thicknesses involved, little bearing wear in ram guiding movementcan be tolerated if the necessary trueness, quality and completed partsurface finish is to be maintained. Furthermore, it is fundamental thatbearing wear and maintenance problems multiply or increasedisproportionately for only slight increases in speed. Thus, the variousforms of ram bearing supports in the prior mechanisms have been agreatly limiting factor for the practical operation thereof and havegreatly limited the speed of operation from that that would beconsidered most desirable.

In the die pack areas of the can body forming mechanisms, the thirdgeneral problem area, proper die and metal part lubrication and coolingmust be maintained and this despite the inherent problems presented withthe increased ram speeds during ram and metal part movement through thevarious dies. Also, not only must the mechanisms providing the properlubrication and cooling be properly integrated within the die pack, butboth the cooling mechanisms and the working portions of the diesthemselves must be properly securely mounted within the die pack forwithstanding the high speed ram operations with the resulting maximumrequired trueness and quality of produced can bodies. Still at the sametime, despite this required provision of proper lubricating and coolingmechanisms with proper support for such mechanisms and the variousmultiple dies within the die pack, all of the combined elements must berelatively easily accessible at the individual die stages, as well asthe total individual die stage assemblies, for efficient servicing andrequired replacement under minimum time conditions unless along downtime delays are to be encountered.

OBJECTS AND SUMMARY OF THE INVENTION It is, therefore, an object of thisinvention to provide an apparatus for forming one piece metallic canbodies wherein the reciprocal ram performing the working operations ismechanically driven to gain inherent advantages of such mechanicaldrive, yet through a unique form of mechanical linkage by pivotal motiontransfer arms between the crankshaft and reciprocal ram, a reducedcomparative speed of ram reciprocal movement and movement reversal isobtained directly approaching and following the ram stroke rearwardreversal for part feeding than the ram speeds directly approaching andfollowing the ram stroke forward reversal for completion of the ramworking operation. According to certain of the principles of the presentinvention, the pivot arms between the crankshaft and the ram areuniquely connected and arranged producing a longer effective drivingpivot arm extension during the forward portions of the ram strokes thanduring the rearward portions thereof so as to produce higher over-allram speeds during such forward portions and reduced over-all ram speedsduring such rearward portions. Thus, maximum speed of operation ismaintained during the working and partial return portion of the ramstrokes, yet reduced ram speed is maintained during the required partfeeding portions of the ram strokes, thereby effectively controllablyvarying the ram speeds to gain maximum speed of operation while stillgaining the predicted uniformity of ram movement inherent in themechanical drive thereof.

It is a further object of this invention to provide an apparatus forforming one piece metallic can bodies wherein the main bearing supportfor the reciprocal ram permits extremely high ram stroke speeds withmaximum trueness but virtually free of wear problems resulting inminimum maintenance and downtime losses. According to certain other ofthe principles of the present invention, the main bearing support forthe reciprocal ram is formed by a unique construction ofhydrostatic-type pressurized oil film bearing assembly preferablyincluding multiple spaced, generally vertically and generallyhorizontally reacting pads acting against corresponding slide surfaceswith continuously pressurized and continuously flowing thickened oilfilms distributed therebetween maintaining the pad surfaces spaced fromthe slide surfaces and pressure oil film supporting the ram aligned bothvertically and horizontally during the ram reciprocal movements. Alsopreferably, the cooperating pad and corresponding slide surfaces arearranged producing force components, taking into account weight, forbalancing the ram both vertically upwardly and vertically downwardly forproper captive horizontal reciprocal movements of the ram, while at thesame time, the cooperating pad and corresponding slide surfaces arearranged producing force components to accomplish the necessarytransverse guiding of the ram.

It is still a further object of this invention to provide an apparatusfor forming one piece metallic can bodies wherein a unique form ofhydrostatic-type pressurized oil film bearing assembly may be mounted ata forward portion of the stationary ram supporting elements on theapparatus and acting directly against a peripheral surface of the ram inorder to give the greatest possible support for the ram rearwardly ofthe die pack and permit a maximum ram stroke despite the necessity ofthe ram projecting forwardly an extended free distance while movingthrough the multiple redraw and ironing die stages. Different from thepreviously discussed main hydrostatic-type pressurized oil film bearingassemblies, this forward hydrostatic-type pressurized oil film bearingassembly preferably includes a sleeve mounted stationary on the mainframe of the apparatus having an inner surface at all times telescopingparts of the reciprocally movable ram and with said inner surface havinga plurality of pressurized oil inlets opening through such inner surfaceand against a peripheral surface of the ram. A constant flow ofconstantly pressurized oil is forced through the sleeve oil inletsdirectly against the ram peripheral surface so as to maintain the sleeveand ram surfaces spaced apart pressure oil film supporting the ramduring the ram reciprocal movements and again permitting the ram highstroke speed with maximum trueness and virtual freedom from wear.

It is also an object of this invention to provide an apparatus forforming one piece metallic can bodies incorporating a unique die packassembly wherein maximum die lubricating and cooling liquid distributionis maintained for efficient die and working part lubrication and coolingdespite the increased ram speeds. According to this portion of theprinciples of the present invention, a particular form of fluid orliquid distribution ring is incorporated in each of the stages of theironing die assemblies, preferably ahead or rearwardly of each of theironing die rings with the distribution ring having an inlet opening oropenings arranged for directing a flow of lubricating and cooling liquidtangentially into the center opening of the distribution ring throughwhich the ram passes. This tangential flow of lubricating and coolingliquid creates a unique form of lubricating and cooling liquidcircumferentially moving ring across the distribution ring ram openingthereby insuring the complete distribution of the liquid over the metalpart being worked and into the particular ironing die ring during theram movement through that particular stage of ironing die assembly.

It is still an additional object of this invention to pro vide anapparatus for forming one piece metallic can bodies incorporating aunique form of die pack assembly wherein each of a plurality ofindividual ironing die assemblies, preferably including an initialredraw die assembly, are each axially registerable with various dieassembly spacers axially therebetween so that the overall diepackassembly may be assembled and disassembled at will and during eachreassembly will always, due to the cooperative registry between thevarious die pack components, reassemble in exact axially alignment. Thevarious individual die rings are radially adjustably aligned in theirindividual die ring assemblies and with this registry between thevarious individual die ring assemblies and their intermediate spacers,the over-all die pack assembly may be disassembled, one die ringassembly axially from its adjacent spacer and adjacent die ringassembly, and reassembled without disturbing the individual die ringradial alignment within any of the individual over-all die ringassemblies, thereby accomplishing maintenance operations in a minimum oftime and avoiding the tedious multiple dowel pin alignments between thevarious die ring assemblies and spacers as has been required in theprior constructions. Still in addition, in each individual die ringassembly, both the individual die ring and the beforementioned liquiddistribution ring are preferably secured in a surrounding centeringring, the radial alignment of such centering ring accomplishing theradial alignment of the die ring, and this subassembly in each die ringassembly may be separately removed from the die ring assembly by removalof a covering plate permitting removal of such subassembly withoutdisturbing the remainder of that individual die ring as sembly withinthe over-all die pack assembly, again reducing maintenance time andexpense to a minimum.

Other objects andadvantages of the invention will be apparent from thefollowing specification and the accompanying drawings which are for thepurpose of illustration only.

BRIEF DESCRIPTION OF THE DRAWINGS FIGS. 1 and 2 are perspective views ofan embodiment of the apparatus for forming one piece metallic can bodiesof the present invention looking from opposite forward side portionsthereof and showing the over-all assembled apparatus;

FIG. 3 is an enlarged, fragmentary, vertical sectional view looking inthe direction of the arrows 3-3 in FIG. 2 and showing a part of the ramdrive;

FIG. 4 is a fragmentary, horizontal sectional view looking in thedirection of the arrows 4-4 in FIG. 3;

FIGS. 5 and 6 are fragmentary, vertical sectional views looking in thedirection of the arrows 5-5 and in the direction of the arrows 6-6,respectively, in FIG. 4;

FIG. 7 is an enlarged, fragmentary, somewhat side elevational viewprimarily of the ram carriage, ram guide assembly and rearward portionof the horizontally reciprocal ram, including a side elevational view ofthe redraw die assembly and positioning means therefor;

FIG. 8 is an enlarged, fragmentary, vertical sectional view looking inthe direction of the arrows 8-8 in FIG. 7 further illustrating the ramcarriage and ram reciprocal support;

FIG. 9 is a view similar to FIG. 8 looking in the direction of thearrows 9-9 in FIG. '7;

FIG. 10 is a fragmentary, top plan view with certain parts removedlooking in the direction of the arrows 10-11) in FIG. 7;

FIG. 1 1 is a fragmentary, vertical sectional view looking in thedirection of the arrows 11-11 in FIG. 10;

FIG. 12 is a view similar to FIG. 11 but showing a more forward portionof FIG. 11 with a portion of the cup-like metal part feeding mechanismpositioned relative to the redrawing die and redrawing die pad, acuplike metallic part in initially fed position with the redrawing diepad in forward working position within the cup-like metallic part, theforward end of the ram entering the redrawing die pad approaching thebottom wall of the cup-like metallic part and the redrawing die ringspaced forwardly of the redrawing die pad;

FIG. 13 is an enlarged, fragmentary, top plan view looking in thedirection of the arrows 13-13 in FIG. 2 primarily showing the die packportion of the apparatus with the cup-like metallic part feedingmechanism added and with a part therein ready for but not yet engaged bythe redrawing die pad, the initial redrawing die ring assembly, aplurality of progressive ironing die ring assemblies, a stripperassembly and a bottom forming die assembly;

FIG. 14 is a fragmentary, vertical sectional view looking in thedirection of the arrows 14-14 in FIG. 13 and showing the individual diering assembly axial registry in the over-all die pack assembly;

FIG. 15 is an enlarged, vertical sectional view looking in the directionof the arrows 15-15 in FIG. 14 and showing an elevation of one of theironing die ring assemblies;

FIG. 16 is a vertical sectional view looking in the direction of thearrows 16-16 in FIG. 15;

FIG. 17 is an enlarged, vertical sectional view taken from FIG. 14 andmore clearly illustrating the stripper assembly portion of the die packassembly of FIG. 14;

FIG. 18 is an enlarged, vertical sectional view looking in the directionof the arrows 18-18 in FIG. 16 and showing the fluid distribution ringassembly in end elevation;

FIG. 19 is an enlarged, fragmentary, vertical sectional view taken fromFIG. 1 l and principally illustrating the forward hydrostatic-typepressurized oil film bearing sleeve forwardly supporting the reciprocalrarn;

FIG. 20 is a fragnentary, end elevational view of the bearing sleeveassembly of FIG. 19 looking in the direction of the arrows 20-20 in FIG.19;

FIG. 21 is an enlarged, fragmentary sectional view looking in thedirection of the arrows 21-21 in FIG. 20;

FIG. 22 is an exploded, perspective view of the ram mounting assemblyand main bearing support showing the pressurized oil supply for thehydrostatic-type pressurized oil film bearing pads thereof;

FIGS. 23 through 27 are somewhat diagrammatic views illustratingprogressive stages of movement of the reciprocal ram through the diepack assembly during the working portion of the ram movement and theredrawing, ironing and bottom forming of a cup-like metallic partresulting in a finished one piece metallic can body, the individual diering assembly axial registry also being shown; and

FIGS. 28 through 31 are somewhat diagrammatic views of the metallic canbody forming apparatus show ing progressive stages of movement of theram drive and the reciprocal ram.

DESCRIPTION OF THE BEST EMBODIIVIENT CONTEMPLATED:

An embodiment of the over-all assembly of the apparatus for forming onepiece metallic can bodies incorporating the principles of the presentinvention is illustrated in FIGS. 1 and 2 and, except as hereinafterspecifically pointed out, is formed of generally standard components andstandard materials appropriate for performing the functions required.The main drive for the can body forming apparatus is supplied by anelectric drive motor 40 through a usual variable speed drive 42, both ofwhich are mounted at an upper portion of a main frame generallyindicated at 44, the variable speed drive in turn through usual beltingdriving a flywheel (not shown) mounted on a main drive shaft 46. Theforegoing driving elements constitute a part of a ram mechanical driveassembly generally indicated at 48 which, with a ram support and guideassembly generally indicated at 50 and a die pack assembly generallyindicated at 52 constitute the major working portions of the apparatus,each of which will be described in detail below.

RAM MECHANICAL DRIVE ASSEMBLY Referring for the moment to FIGS. 1through 6, the ram mechanical drive assembly 48 further includes themain drive shaft 46 projecting transversely into the interior of themain frame 44 and mounting a pair of spaced drive gears 54 which areoperably engaged with a pair of spaced bull gears 56. A crank arm 58 issecured to each of the facing sides of the bull gears 56 projectingradially of that particular bull gear with radially outer ends of thecrank arms mounting an axially extending crank pin 60 therebetween. Therearward end of a transfer arm 62 is rotatably connected to the crankpin 60 axially between the crank arms 58 and the forward end of thetransfer arm is rotatably connected to an axially extending connectingpin 64 mounted intermediate and preferably generally midway of thegenerally vertically extending length of a bifurcated drive arm 66.

The lower end of the drive arm 66 spaced below the connection of thetransfer arm 62 thereto is pivotally mounted on the main frame 44 andthe upper end of the drive arm spaced above the transfer arm ispivotally connected to the rearward end of a drive rod 68. The drive rod68 extends generally longitudinally forwardly into an intermediateportion of a slide assembly 70 forming a part of the ram support andguide assembly 50 as seen, for instance, in FIG. 10, the slide assemblybeing shown in FIG. 22 removed from the apparatus, all of which will behereinafter described more in detail. For purposes of presentdiscussion, it is sufficient to state that the slide assembly 70 isforwardly and rearwardly longitudinally reciprocal on the main frame 44and at the forward end thereof secures the rearward end of alongitudinally extending and likewise longitudinally forwardly andrearwardly reciprocal ram 72 which is cylindrical in configuration.

Thus, now also referring to the diagrammatic showing in FIGS. 28 through31 and considering the center mounting of the bull gears 56 andtherefore the crank arsm 58 on stub-like crankshaft 74 as shown in FIG.5, it is seen that the crankshaft 74 in its rotation drives thecrankarms 58, which crankarrns are connected through a plurality orseries of pivot arms, the transfer arm 62, drive arm 66 and drive rod68, to the ram 72 for producing generally horizontally reciprocalforward and rearward movement of the ram. Also considering, and again aswill be hereinafter described more in detail, that the forward portionsor to the right as shown in FIGS. 28 through 31 of the reciprocalstrokes of the ram 72 are the working portions thereof and the rearwardportions or to the left as shown in FIGS. 28 through 31 are the partfeeding portions thereof, it will be seen that the ram stroke workingportions are at a higher rate of speed than are the part feedingportions thereof due to the particular connecting and arrangement of thepivot arms between the crankshaft 74 and the ram 72. During the forwardof rotation or right side rotation around the crankshaft 74 of the crankarms 58, the forward end of transfer arm 62 is extended further from theradial outward end of the crank arms increasing the leverage on thedrive arm 66 so as to increase the speed thereof, whereas in therearward (left side) 180 of rotation of the crank arms, the effectivelever arm to the drive arm 66 is shorter due to the doubling of thecrank arms 58 on the transfer arm 62, thereby reducing the effectivelever arm movement to the drive arm 66 and therefore the ram 72.

Furthermore, as can be clearly seen from FIGS. 5, 6 and 28 through 31,with the crank arms 58 secured for rotation with the crankshaft 74 andthe transfer and drive arms 62 and 66 pivotally connected thereto, it isobvious that the forward movement of the ram 72 from the ram strokerearward reversal toward the ram stroke forward reversal is in aparticular changing speed pattern of movement which is the same, butexactly reversed, in the ram movement from the forward reversal back tothe rearward reversal. This is to say, with the particular pivot armconnection, from the slower rearward reversal, the ram is movedforwardly in a particular changing speed pattern to the faster forwardreversal and then begins and carries through an exact reversal of thischanging speed pattern of movement from he forward reversal back to therearward reversal, always being the same for a constant speed of thecrankshaft 74.

As is more clearly shown diagrammatically in FIGS. 28 through 31, inFIG. 28, the drive arm 66 is in its rearrnost pivoted position drawingthe ram 72 to its rearrnost position and it is seen that the transferarm 62 is at its rearrnost point of rotation by the crankshaft 74thereby constituting a minimum length lever arm. In FIG. 29, the drivearm 66 and ram 72 have moved forwardly and the transfer arm 62 isentering its forward 180 of rotation about the crankshaft 74 so that theeffective lever arm to the drive arm and ram has increased in lengthfrom the FIG. 28 position and will continue to increase in length. InFIG. 30, the transfer arm 62 has reached its maximum forward positionmoving the drive arm 66 pivotally to its forwardmost position andlikewise the ram 72, whereas in FIG. 31, the transfer arm and ram aremoving rearwardly and the effective lever arm thereon in decreasing andwill continue to decrease until it reaches the position shown in FIG.28.

With this unique drive connection to the ram 72, the ram moves at ahigher rate of speed during the forward working portions of the ramstrokes and at a slower relative speed during the rearward part feedingportions of the ram strokes. Despite the drive to the ram 72 beingpurely mechanical, therefore, a high rate of ram speed is maintainedduring the forward portions and reversal of the ram forward and rearwardreciprocal stokes, yet the ram moves at a relative reduced speed duringthe rearward portions and reversal of the ram strokes. This provides theram strokes during the working portions thereof possible at maximumspeed and reduced time while still providing slower speed and increasedtime during the ram stroke part feeding portions, the latter requiringsuch increased time for proper part positioning.

RAM SUPPORT AND GUIDE ASSEMBLY According to the broad principles of thepresent invention, the ram support and guide assembly provides bothvertically and horizontally reacting force components for supporting theram and its support or mount longitudinally movable in the reciprocalstrokes, said force components preferably effectively reacting in alldegrees of vertical and horizontal. The particular embodimentillustrated includes the ram support and guide assembly 50 as best seenin FIGS. 7 through 12 and FIGS. I9 through 22. Furthermore, the majorportion of the ram support and guide assembly 50 is formed by a mainhydrostatic-type pressurized oil film bearing assembly principallycomprised of the previously mentioned ram slide assembly 70 and atransversely spaced pair of stationary slides or slide plates 76 bestseen in FIGS. 7 through 16, while an auxiliary portion of the ramsupport and guide assembly 50 is formed by a forward hydrostatic-typepressurized oil film bearing assembly principally comprised of astationary bearing sleeve 78 best seen in FIGS. 19 and 20 mounted withinand secured stationary to the main frame through a cylinder and bearingassembly 80. As

previously stated, the rearward extremity of the ram 72 is secured toand movable with the slide assembly 70 projecting longitudinallyforwardly from a forward surface thereof, such securement being obtainedthrough an adjustable collar assembly 82.

The ram slide assembly 74) is shown removed from the apparatus in FIG.22 and without the ram 72 mounted thereon, such assembly including aparticularly formed ram support and guide assembly 50 mounting aplurality of sets of vertically spaced, vertically upwardly anddownwardly acting bearing pads 86, and sets of transversely spaced,horizontally oppositely acting bearing pads 88. As shown, each of thevertically acting bearing pads 86 has a horizontal annular face surface90 surrounding a central oil inlet 92, and each of the horizontallytransversely acting bearing pads 38 has a vertical annular face surface94 surrounding a central oil inlet 96, the oil inlets each beingconnected through a pressurized oil system 98 downwardly through apivotal oil supply linkage MM) and an oil pressure pump 1102 (FIGS. 1and 2) to a source of oil supply. As is also shown, the verticallyacting bearing pads 66 of each set are positioned with the upper padacting downwardly and the lower pad acting upwardly, there beingtransversely aligied vertically acting bearing pad sets spacedtransversely outwardly from the longitudinal axis of the ram 72 at eachof the forward and rearward extremities of the slide assembly frame 64.Also, the horizontally transversely acting bearing pads 88 of each offorward and rearward sets thereof include one pad acting oppositelyoutwardly from either side of the slide assembly frame 84.

As shown in FIGS. 7 through 10, the slides or slide plates 76 aresecured stationary on the main frame 44, there being two transverselyuniformly spaced apart throughout the longitudinal extents thereof andeach presenting a transversely inwardly and longitudinally extending,upwardly facing horizontal surface 164i and downwardly facing horizontalsurface 106, such horizontal surfaces terminating transverely inwardlyin longitudinally extending and transversely inwardly facing verticalsurfaces 166. Thus, as shown generally, for instance, in FIG. 10 andparticularly in FIG. 9, the slide assembly is longitudinally slidablymounted on the slide plates 76 with the horizontally facing surfaces 96of the vertically downwardly acting bearing pads 86 adjacent the slideupwardly facing horizontal surfaces 104 and the horizontally facingsurfaces 90 of the vertically upwardly acting bearing pads 86 adjacentthe slide downwardly facing horizontal surfaces 106 with the verticallyfacing surfaces 94 of the horizontally transversely outwardly actingbearing pads 88 adjacent the slide transversely inwardly facing verticalsurfaces 108 so as to capitivate the slide assembly 70 for guidedhorizontally slidable movement longitudinally along the slide plates 76.At the same time, during such movement longitudinally forwardly andrearwardly of the slide assembly 70 along the slide plates 76 andcarrying the ram 72 longitudinally forwardly and rearwardly therewith,constantly pressurized and constantly flowing oil is directed from thevarious bearing pad oil inlets 92 and 96 creating a constantlypressurized, thickened oil film between the various facing bearing padand slide plate surfaces suspending the slide assembly 70 slidablymovable along the slide plate 76.

In the unique form of the hydrostatic-type pressurized oil film bearingassemblies of the present invention as created by the coacting slideassembly 70 and slide plates 76 just described, and as is true of thesomewhat similarly acting forward hydrostatic-type pressurized oil filmbearing assembly formed in part by the bearing sleeve 78 as will behereinafter described, there is a constantly pressurized and constantlyflowing oil film created from outside oil pressure at all times betweeneach of the slide assembly bearing pad and slide plate facing surfacesactually oil film suspending, and as a consequence of a particular padand slide plate surface positioning and oil pressure regulating,creating a selfcentering of the slide assembly 70 on the slide plates76, which prevents any possible metal to metal contact despite theobvious horizontal and transverse loads supported by such oil films.Furthermore, this oil film suspension is not dependent on relativemotion between the coacting and facing surfaces of the slide assembly 70and the slide plates 76, but will rather be present whether the coactingand facing surfaces are stationary or moving relative to each other.This hydrostatic-type pressurized oil film suspension between thecoacting and facing surfaces should be differentiated from the usualform of hydrodynamic bearings wherein a thickened film of oil isdependent on the movement and speed between the coacting and facingsurfaces and wherein a decrease in the relative speeds between thesurfaces will cause a sinking of the oil film causing at least periodicmetal to metal contact.

Further in the present unique form of hydrostatictype pressurizedthickened oil film assemblies herein involved, the oil pressures to thevarious oil inlets are regulated to obtain preferably substantialself-centering of the slide assembly 70 horizontally longitudinallymovable along the slide plates 76. Furthermore, in the particularembodiment shown, the clearance between the coacting and facing surfacesof the bearing pads 86 and 88 and the slide plates 76 is preferably inthe order of two thousandths inches and the oil film pressure constantlymaintained by constant flow is in the order of 600 to 800 pounds persquare inch at the bearing pad and slide plate surfaces. Withhydrostatic-type pressurized thickened oil film bearing assemblies ofthis form, a greater clearance between the coacting and facing surfaceswill create a softer, less load supporting bearing where as a lesserclearance between such surfaces will create a stiffer bearing, but inany case, different from the conventional hydrodynamic bearings involvedwith sinking oil films and metal to metal contact, with thehydrostatic'type oil bearings of the present invention, there willalways be an oil film suspension between the various coacting and facingsurfaces regardless of motion or the usual clearances.

More particularly to the construction of the bearing pads 86 and 88 ofthe ram slide assembly 70, as shown, for instance, in FIG. 22, each ofthe pad surfaces 90 and 94 is a raised flat surface forming a quitebroad raised flat surface area which surrounds and terminates inwardlyin a recessed oil inlet area having either the oil inlet 92 or 96. Also,as clearly shown in FIG. 22, the portions of the ram slide assembly 70outwardly of the peripheries of the pad surfaces 90 and 94 are recesseddue to the raising of such pad surfaces. With the relatively broad andflat pad surfaces 90 and 94, the surface areas thereof being far greaterthan the individual oil inlet areas thereof, and with these pad surfacesbeing raised and isolated from the remainder of the ram slide assembly70, these pad surfaces with the beforedescribed pressurized oil filmsthereon form the sole support for the ram slide assembly 70 on the mainframe slide plates 76 and insure that the hydrostatictype pressurizedthickened oil films will be the only bearings between the ram slideassembly 70 and the main frame slide plates 76 during movementtherebetween as described.

Thus, the ram support and guide assembly 50 including the slide plates76 and the vertically and horizontally transverely acting bearing pads86 and 88 effectively provide force components effectively reacting inall degrees of vertical and horizontal by combining the reaction forcesof the various opposed horizontal and vertical surfaces and despite thefact that in this particular embodiment such surfaces are only generallystraight horizontal and vertical.

The forward hydrostatic-type pressurized oil film bearing assembly forsupporting the ram reciprocally movable forwardly and rearwardlyhorizontally along the main frame 44 in the ram forward and rearwardstrokes, as hereinbefore stated, includes the bearing sleeve 78 which ismounted stationary on the main frame in the cylinder and bearingassembly 80, said cylinder and bearing assembly being positioned on themain frame forwardly of the forward and rearward movement of thehereinbefore described slide assembly and partially overlying theforward termination of the slide plates 76 as can be seen generally inFIGS. 7 and 10. As is particularly shown in FIGS. 1 1 and 19, thebearing sleeve 78 is secured at the rearward portion of the cylinder andbearing assembly 80 at all times telescoping an axially orlongitudinally intermediate portion of the ram 72, the ram beinglongitudinally forwardly and rearwardly slidable relative thereto andhydrostatic-type pressurized thickened oil film supported thereby duringsuch movement. The particulars of formation of the bearing sleeve 78with its constant pressun'zed oil supply and exhaust are shown in FIGS.19 through 21, a portion of the ram 72 being shown in phantom lines inits positioning through the bearing sleeve in FIG. 19.

As shown, the bearing sleeve 78 is hollow cylindrical having fourequally circumferentially spaced and axially or longitudinally elongatedoil inlet openings or slots radially therethrough and opening radiallyin wardly against a periphery 112 of the cylindrical ram 72. An oilinlet conduit 114 is formed through the cylinder and bearing assembly 80to each of the oil inlet slots 110 for providing a supply of pressurizedoil from the previously described pressurized oil system originating atthe oil pressure pump 102 (FIGS. 1 and 2), and a pair of oil outletconduits 116 are formed from just forwardly of the bearing sleeve 78rearwardly through the cylinder and bearing assembly as best seen inFIGS. 20 and 21. In the preferred form shown, the oil inlet slots 110extend axially or longitudinally a majority of the axial or longitudinallength of the bearing sleeve 78.

Thus, during the horizontally forwardly and rearwardly reciprocalmovements of the ram 72, intermediate portions of the ram are supportedon hydrostatictype pressurized thickened oil films of the same generalcharacteristics as discussed relative to the main bearing assemblyformed by the slide assembly 70 and the slide plate 76, in this forwardbearing assembly, the pressurized oil constantly flowing and constantlypressurized flowing through the oil inlet conduits 114, through the oilinlet slots 110 against the ram periphery 112 and outwardly through theoil outlet conduits 116, thereby providing a unique bearing supportspaced forwardly of the main bearing support for the ram 72 in itsrelatively long longitudinal extension forwardly through the die packassembly 52 in the ram forward and rearward reciprocations. The forwardhydrostatic-type pressurized oil film bearing assembly including thebearing sleeve 78, therefore, likewise effectively provides forcecomponents efiectively reacting in all degrees of vertical andhorizontal by continuing the opposed vertical and horizontal forces fromthe sleeve slots 110 against the ram periphery 112 to additionallysupport the ram 72, despite the fact that in this particular embodimentsuch forces are only generally direct vertical and horizontal.

As is also shown in FIG. 19, the cylinder and bearing assembly 80includes a wiper seal assembly 118 forwardly of the bearing sleeve 78and the forward ends of the oil outlet conduits 1 16 for separating thepressurized oil supply to the bearing sleeve from cooling andlubricating liquids supplied to the die pack assembly 52 and necessarilycovering the ram periphery 112 during the travel of the ram reciprocallythrough the die pack assembly.

Referring particularly to FIGS. 7 through 12, a further important partof the cylinder and bearing assembly 88 is formed by pairs oftransversely spaced upper and lower air cylinder assemblies generallyindicated at 120 each including a cylindrical air piston 122, with theair pistons being forwardly and rearwardly reciprocal in such assemblyand being shown forwardly extended in FIGS. 7 and 10 through 12. Atransversely extending forward hold down plate 124 is secured to theforward end of the air pistons 122 and has a forwardly projecting,hollow cylindrical draw pad 126 secured thereto, said draw pad beingaxially or longitudinally aligned with the ram 72 and receiving the ramtelescopically therethrough during the forward and rearward reciprocalmovements of the ram, all for a purpose to be hereinafter described. Theair pistons 122 are urged forwardly extended by a constant supply ofpressurized air to thereby urge the forward hold down plate 124 and thedraw pad 126 forwardly, and the rearward movement of the air pistonstelescoped rearwardly within the cylinder and bearing assembly 811 iscontrolled by two pairs of transversely spaced, upper and lower pullrods 128 forwardly connected to the hold down plate 124 spaced outwardlyof the air pistons and extending rear wardly above and beneath the slideplates 76 as best seen in FIGS. 7 through 18.

The rearward ends of the pull rods 128 are secured to a rear crosshead131) which is forwardly and rearwardly slidable on guideways 132 mountedon the main frame 44, and on a forward surface of the rear crossheadadjacent the connections thereof to the pull rods are four bumpers 134rearwardly aligned with four oil actuated shock absorbers 136 projectingrearwardly from and movable with the previously described slide assembly70 of the main ram bearing assembly. Thus, as the slide assembly 711 ofthe ram main bearing assembly moves forwardly moving the shock absorbers136 forwardly away from the bumpers 134, the air pistons 122 of thecylinder and bearing assembly 80 will move the forward hold down plate124 and the draw pad 126 to their forward extended positions as shown,and as the slide assembly moves rearwardly ultimately engaging the shockabsorbers 136 rearwardly with the bumpers 134 on the rear crosshead1311, the pull rods 128 will be moved rearwardly withdrawing orrearwardly telescoping the pistons into the cylinder and bearingassembly and rearwardly withdrawing the draw pad 126. As will also behereinafter described more in detail, the timing of the movement of theram 72 and the forward movement of the draw pad 126 is such that thedraw pad moves forwardly ahead of the leading or forward end of the ramso that the draw pad first forwardly positions followed by the forwardend of the ram moving forwardly therethrough.

DIE PACK ASSEMBLY As shown in FIGS. 1 and 2, the die pack assembly 52 ismounted on the main frame 44 forwardly of the ram support and guideassembly 58 for receiving the ram 72 horizontally reciprocally forwardlyand rearwardly through a major portion thereof, the particulars of thedie pack assembly being best seen in FIGS. 13 through 18. As shown inFIGS. 13 and 14, the die pack assembly 52, starting at the rearward orleft end and moving axially or longitudinally toward the forward end,includes a redraw die ring assembly 138, a register ring 140, a firstironing die ring assembly 142, a spacer ring 144, a second ironing diering assembly 146, a spacer ring 148, a third ironing die ring assembly158, a spacer ring 152 and a stripper assembly 154, all of which aresecured axially or longitudinally stacked, one axially or longitudinallyadjacent the next. The die pack assembly 52 also includes a doming orbottom forming die assembly 156 spaced axially or longitudinallyforwardly from the stripper assembly 154 on supports 158 and forming theforward termination ofthe die pack assembly.

The redraw die ring assembly 138 supports a redraw die ring 160 and thefirst, second and third ironing die ring assemblies 142, 146 and 151)support first, second and third ironing die rings 162, 164 and 166respectively, all of said die ring assemblies being similar by theinclusion of mechanism for centering the various die rings for properaxial or longitudinal alignment with the centerline of the ram 72. Also,all of the die ring assemblies are preferably formed with a particularconstruction permitting selective upward removal of a portion of theassembly including the particular die ring thereof after pivoting of acover for access at the upper portion of the die pack assembly 52without complete disassembly thereof, and at least the first, second andthird ironing die ring assemblies 142, 146 and 150 are formed with aparticular fluid distribution ring therein for the distribution ofcooling and lubricating liquids during the operation of the apparatus.

For illustrating such die ring assembly construction,v

the second ironing die ring assembly 146 is illustrated in detail inFIGS. 15, 16 and 18, and includes a main body 168 supporting axiallyspaced wear rings 172 axially between which is vertically slidablysupported the assembly of an outer centering ring 174 telescoping acooling and lubricating fluid distribution ring 176 secured at therearward portion thereof and the second ironing die ring 164 resilientlymounted through a resilient O-ring 178 at the forward portion thereof.As shown, the assembly of the centering ring 174, fluid distributionring 176 and resilient O-ring 178 is vertically slidably supported inthe main body 168 and is accessible for removal by pivoting of cover181) along with centering screw mechanism 182 therein, said cover beingretained in working closed position during operation of the apparatus byhand screws 184 removably secured downwardly into the main body 168.Thus, when maintenance operations are required on the particular diering or the particular fluid distribution ring where included, it ismerely necessary to selectively release the hand screws 184 and pivotthe cover open for slidable removal of the assembly of, in this case,the centering ring 174, the fluid distribution ring 176 and the secondironing die ring 164 for free access to the die ring and fluiddistribution ring, the assembly being replaced in working position by amere reversal and refastening of the hand screws 184.

The fluid distribution ring 176 is, of itself, a unique formation givingvastly improved cooling and lubricating liquid distribution over theperiphery of the ram 72 as it moves longitudinally therethrough and ascarried to the various die rings by such ram movement. As shown in FIGS.16 and 18, the fluid distribution ring 176 includes an inner annularportion 186 having an inner diameter spaced larger than the periphery ofthe ram 72 and an outer annular portion 188 spaced outwardly from saidinner annular portion forming an annular fluid channel 1% therebetweenwhich is closed axially rearwardly by the rearward of the wear rings 172as seen in FIG. 16. Cooling and lubricating liquid is fed to the fluidchannel 190 by a fluid inlet 192 and preferably a pair or more ofequally circumferentially spaced, tangential openings 194 are formedthrough the inner annular portion 186 and open tangentially into thecenter opening thereof so that the cooling and lubricating liquidpassing interiorly of the fluid distribution ring 176 flows therein in atangential direction circumferentially around the center opening of saidring producing a circumferentially moving annulus or ring of cooling andlubricating liquid sometimes virtually centrally closed, through whichthe ram 72 passes insuring a complete and total coverage of said ram andproper distribution to the various die rings, as well as over theparticular metal part being formed and as will be hereinafter described.

As shown in FIGS. 13 and 14 and in enlarged detail in FIG. 17, thestripper assembly 154 of the die pack assembly 52 also includescentering screw mechanisms 196 which bear inwardly against a two pieceretainer ring 198 having an inner axially or longitudinally extending,but radially or transversely outwardly angled cam surface 200, that is,the surface angling from a lesser diameter rearwardly toward the thirdironing die ring assembly 150 to a great diameter forwardly toward thedoming or bottom forming die assembly 156. A limit ring 202 ispositioned partially outwardly in the retainer ring 198 and extendsinwardly of the inner cam surface 200 projecting into outwardly opening,circumferential slots 204 of a plurality of stripper segments 206. Thestripper segments 206 have outer cam surfaces 208 oppositely matchingthe inner cam surface 200 of the retainer ring 198, forwardly inwardlyangled inner surfaces 210, and in their plural assembly form an inwardlyrearwardly angled, annular slot 212 receiving a garter spring 214.

The arcuate lengths of the stripper segments 206 are such that when thesegments are normally rearwardly positioned radially inwardly alignedwith the retainer ring 198 as shown in FIG. 17, the segmentscircumferentially abut and the inner diameter formed by the innersurfaces 210 thereof is at a minimum. When, however, a metallic partpasses therethrough from rearwardly to forwardly thereof having an outerdiameter larger than said segment minimum inward diameter, thesesegments move forwardly and outwardly along the retainer ring inner camsurface 200 as permitted by the garter spring 214 so as to increase ininner diameter and permit the passage of the larger diameter metallicpart therethrough. Upon the larger diameter metallic part passingforwardly beyond these stripper segments 206, the segments areimmediately urged rearwardly along the retainer ring inner cam surface200 to a lesser diameter so that when the metallic part is attempted tobe moved reversely rearwardly through the opening formed by the strippersegments, the segments will engage the same, all for a usual strippingpurpose as will be hereinafter more clearly explained.

The final portion of the die pack assembly 52 is formed by the doming orbottom forming die assembly 156 spaced forwardly of the stripperassembly 154 as shown in FIGS. 13 and 14. The bottom forming dieassembly 156 again includes centering screw mechanisms 216, but moreimportantly centrally mounts a bottom forming die 218 which facescentrally, axially or longitudinally rearwardly and rearwardly presentsan arcuately domed working surface 220. The domed working surface 220 ofthe bottom forming die 218 is received in a recess (not shown) at theforward end of the ram 72 when the ram reaches its forward maximumtravel through the die pack assembly 52 in its forward stroke as willalso be hereinafter explained more in detail.

Another important feature of construction of a major part of the diepack assembly 52 is the fact that all of the redraw die ring assembly138, the first ironing die ring assembly 142, the second ironing diering assembly 146, the third ironing die ring assembly 150 and thestripper assembly 154 all axially or longitudinally register with theirrespective intermediate register and spacer rings 140, 144, 148 and 152,respectively. That is to say, all of the redraw, first ironing, secondironing, and third ironing die ring assemblies 138, 142, 146 and 150,and the stripper assembly 154 have either axially opening recesses oraxial projections, either full circular or annular axially orlongitudinally meeting with their respective intermediate register andspacer rings 140, 144, 148 and 152 so that each of the die ringassemblies and this stripper assembly is in full axial registry with allothers of said die ring and stripper assemblies in the over-all die packassembly 52 permitting quick disassembly of the die pack assembly foraccess to any part thereof and the reassembly will again bring allindividual assemblies into the exact same axially or longitudinalalignment, one with the other and the various centering screw mechanismsin each assembly need not be disturbed. The only dowel pin connectionrequired within the die pack assembly 52, therefor, is an individualdowel pin projecting between the various assemblies and their adjacentregister or spacer ring to prevent rotation therebetween as will behereinafter described more in detail, but such dowel pins not servingany axial or longitudinal alignment function as has been required withmultiple dowel pins in the prior constructions.

Referring more particularly to FIGS. 14 and 23 through 27, the redrawdie ring assembly 138 is provided with an exactly centered, circularrecess 222 receiving a major part of the register ring 140 axially, inperfect fit and registry, therein, the remaining portion of the registryring axially toward the first ironing die ring assembly 142 beingreceived in a similar circular, exactly centered and exactly fittingrecess 224 of the first ironing die ring assembly 142. Projectingoppositely from the first ironing die ring assembly 142 axially towardthe spacer ring 144 is an exactly centered, annular projection 226received axially into an exactly fitting and exactly centered annularrecess 228 of the next axially adjacent spacer ring 144. Ananti-rotation dowel pin 230 is positioned axially between the registerring 140 and the first ironing die ring assembly 142 while a dowel pin232 is similarly received between the first ironing die assembly 142 andthe spacer ring 144, the latter dowel pin 232 projecting from the areaof the fust ironing die ring assembly forming the annular projection 226and into the area of the spacer ring 144 within the annular recess 228.

The spacer ring 144 has an axially opposite annular recess 234 exactlyaxially aligned, but oppositely axially facing from the annular recess228 receiving an exactly matching annular projection 236 of the secondironing die ring assembly 146, an axially opposite and axially alignedannular projection 238 of the second ironing die ring assembly 146 beingreceived exactly

1. In metal forming apparatus of the type having a main frame mounting alongitudinally reciprocal ram driven by a rotating crankshaft andmovable in forward and rearward strokes with forward and rearwardreversals between said strokes, said ram being adapted for having ametal part positioned to be engaged thereby during a rearward portionand said rearward reversal of said ram strokes and for engaging andforming said metal part during a more forward portion of said strokes;the improvements comprising: drive transfer means including a pluralityof pivot arms connected one to another between and to said crankshaftand ram for transferring said crankshaft rotations into said ramreciprocal forward and rearward strokes and into a reduced comparativespeed of ram reciprocal movement and movement reversal directlyapproaching and following said ram stroke rearward reversal thandirectly approaching and following said ram stroke forward reversal,said pivot arm connection in said drive transfer means reciprocallydriving said ram in a particular changing speed pattern of movement fromsaid ram stroke rearward reversal forwardly to said ram stroke forwardreversal and in an exactly reverse changing speed pattern of movementfrom said ram stroke forward reversal rearwardly to saiD ram strokerearward reversal.
 2. Metal forming apparatus as defined in claim 1 inwhich said drive transfer means includes said plurality of pivot armsbeing connected forming a longer effective driving pivot arm extensionbetween said crankshaft and ram directly approaching and following saidram stroke forward reversal then directly approaching and following saidram stroke rearward reversal providing a reduced comparative speed ofram reciprocal movement and movement reversal directly approaching andfollowing said ram stroke rearward reversal than directly approachingand following said ram stroke forward reversal.
 3. Metal formingapparatus as defined in claim 1 in which said pivot arms of said drivetransfer means include a crank arm secured to and extending radiallyfrom said crankshaft, a transfer arm having a rearward end pivotlyconnected to an outer end of said crank arm and a forward end extendingat all times forwardly of said crank arm, means pivotly connecting saidtransfer arm forward end to said ram.
 4. Metal forming apparatus asdefined in claim 1 in which said pivot arms of said drive transfer meansinclude a crank arm secured to said crankshaft and extending radiallytherefrom, a transfer arm pivotly connected to an outer end of saidcrank arm and having a forward end at all times spaced forwardly of saidcrank arm, a drive arm having a lower end pivotly secured to said mainframe, said transfer arm forward end being pivotly connected to saiddrive arm intermediate upward extension of said drive arm, means pivotlyconnecting an upper portion of said drive arm to said ram, said drivearm upper portion being spaced above said drive arm pivotal connectionto said transfer arm forward end.
 5. Metal forming apparatus as definedin claim 1 in which said ram is mounted on a ram carriage and is movablegenerally horizontally in said forward and rearward strokes by forwardand rearward movements of said ram carriage; and in whichhydrostatic-type pressurized oil film bearing assemblies include ramcarriage and main frame oil bearing parts supporting said ram carriageon said main frame during said ram and ram carriage generally horizontalreciprocal movements, said ram carriage oil bearing parts being securedmovable with said ram carriage and moving relative to said main frameoil bearing parts secured stationary on said main frame, one of said ramcarriage and main frame oil bearing parts including slides havingsurfaces thereon parallel to said ram movements, and the other of saidram carriage and main frame oil bearing parts including spaced padshaving flat surfaces thereon parallel to said ram movements, said padsbeing positioned with said pad surfaces at all times at least partiallygenerally vertically facing and adjacent said slide surfaces,pressurized oil inlets opening through each of said pad surfaces andconnected to pressurized oil supply means distributing constantlyflowing and pressurized, thickened oil films through said inlet over andbetween said pad and slide facing surfaces maintaining said pad surfacesspaced from said slide surfaces and pressure oil film supporting saidram carriage during said ram and ram carriage reciprocal movements, atleast certain of said ram oil bearing parts being positioned exertingvertical force components through said oil films acting generallyvertically downwardly against opposed upward force components of facingof said main frame oil bearing parts providing support at least byvertical force components of said ram horizontally movable on said mainframe, each of said pads being comprised of a raised flat surface areaconstituting said pad surface horizontally isolated from all surroundingsurfaces, said each pad surface surrounding and terminating inwardly inan oil inlet area having said oil inlet, the total of said pad surfacearea being greater than said oil inlet area for each pad, said isolatedpad surfaces with said pressurized oil films thereon against said slidessupporting saiD ram carriage on said main frame during said horizontallyreciprocal movement.
 6. Metal forming apparatus as defined in claim 1 inwhich said ram is mounted on a ram carriage and is generallyhorizontally reciprocal on said main frame movable in said forward andrearward strokes by forward and rearward strokes of said ram carriage;and in which hydrostatic-type pressurized oil film bearing assembliesinclude ram carriage and main frame oil bearing parts supporting saidram carriage on said main frame during said ram and ram carriagegenerally horizontal reciprocal movements, said ram carriage oil bearingparts being secured movable with said ram carriage and moving relativeto said main frame oil bearing parts secured stationary on said mainframe, one of said ram carriage and main frame oil bearing partsincluding slides having at least partially generally upwardly anddownwardly facing surfaces thereon parallel to said ram movements, theother of said ram carriage and main frame oil bearing parts includinggenerally horizontally spaced sets of generally vertically spaced padswith said pads having flat surfaces thereon parallel to said rammovements, said vertically spaced pads of each set being positioned withsaid surfaces of one pad adjacent and generally downwardly facing saidslide upwardly facing surfaces and said surfaces of the other padgenerally upwardly facing said slide downwardly facing surfaces,pressurized oil inlets opening through each of said pad horizontalsurfaces and connected to pressurized oil supply means distributingconstantly flowing and pressurized, thickened oil films through saidinlet over and between said pad and slide facing surfaces maintainingsaid pad surfaces spaced from said slide surfaces and pressure oil filmsupporting said ram carriage by at least both vertically upward anddownward force components during said ram and ram carriage reciprocalmovements to thereby support said ram horizontally movable on said mainframe, each of said pads being comprised of a raised flat surface areaconstituting said pad surface horizontally isolated from all surroundingsurfaces, said each pad surface surrounding and terminating inwardly inan oil inlet area having said oil inlet, the total of said pad surfacearea being greater than said oil inlet area for each pad, said isolatedpad surfaces with said pressurized oil films thereon against said slidessupporting said ram carriage on said main frame during said horizontallyreciprocal movement.
 7. Metal forming apparatus as defined in claim 1 inwhich said ram is mounted on a ram carriage and is generallyhorizontally reciprocal on said main frame movable in said forward andrearward strokes by forward and rearward strokes of said ram carriage;and in which hydrostatic-type pressurized oil film bearing assembliesinclude ram carriage and main frame oil bearing parts supporting saidram carriage on said main frame during said ram and ram carriagegenerally horizontal reciprocal movements, said ram carriage oil bearingparts being secured movable with said ram carriage and moving relativeto said main frame oil bearing parts secured stationary on said mainframe, said main frame oil bearing parts including slides havinggenerally upwardly and downwardly facing surfaces thereon parallel tosaid ram movements, said ram carriage oil bearing parts including setsof generally vertically spaced pads generally transversely horizontallyspaced at opposite sides of a longitudinal axis of said ram, each ofsaid pads having a flat surface thereon parallel to said ram movements,one of said pads of each of said vertically spaced sets being positionedwith one pad surface generally downwardly facing said slide upwardlyfacing surfaces and the other pad surfaces generally facing said slidedownwardly facing surfaces with a slide spaced generally verticallytherebetween, pressurized oil inlets opening through each of said padsurfaces and connected to pressurized oil supply means distributingconstantly flowing anD pressurized, thickened oil films through saidinlet over and between said pad and slide facing surfaces maintainingsaid pad surfaces spaced from said slide surfaces and pressure oil filmsupporting said ram carriage by at least both vertically upward anddownward force components during said ram and ram carriage reciprocalmovements to thereby support said ram horizontally movable on said mainframe, each of said pads being comprised of a raised flat surface areaconstituting said pad surface horizontally isolated from all surroundingsurfaces, said each pad surface surrounding and terminating inwardly inan oil inlet area having said oil inlet, the total of said pad surfacearea being greater than said oil inlet area for each pad, said isolatedpad surfaces with said pressurized oil film thereon against said slidessupporting said ram carriage on said main frame during said horizontallyreciprocal movement.
 8. Metal forming apparatus as defined in claim 1 inwhich said ram is mounted on a ram carriage and is movable generallyhorizontally in said forward and rearward strokes by forward andrearward strokes of said ram carriage; in which hydrostatic-typepressurized oil film bearing assemblies include ram carriage and mainframe oil bearing parts supporting said ram carriage on said main frameduring said ram and ram carriage generally horizontal reciprocalmovements, said ram carriage oil bearing parts being secured movablewith said ram carriage and moving relative to said main frame oilbearing parts secured stationary on said main frame, one of said ramcarriage and main frame oil bearing parts including slides havingsurfaces thereon parallel to said ram movements, the other of said ramcarriage and main frame oil bearing parts including spaced pads havingflat surfaces thereon parallel to said ram movements, said pads beingpositioned with said pad surfaces at all times facing and adjacent saidslide surfaces, pressurized oil inlets opening through each of said padhorizontal surfaces and connected to pressurized oil supply meansdistributing constantly flowing and pressurized thickened oil filmsthrough said inlet over and between said pad and slide facing surfacesmaintaining said pad surfaces spaced from said slide surfaces andpressure oil film supporting said ram carriage during said ram and ramcarriage reciprocal movements, said ram carriage oil bearing parts beingpositioned and through said pressure oil films producing vertical andtransversely opposite horizontal force components acting generallyvertically downwardly horizontally transversely opposite againstcorrespondingly facing and oppositively acting of opposed vertical andtransversely opposite horizontal force components of said main frame oilbearing parts providing support at least by vertical forces and opposedtransverse forces of said ram carriage horizontally movable on said mainframe, each of said pads being comprised of a raised flat surface areaconstituting said pad surface horizontally isolated from all surroundingsurfaces, said each pad surface surrounding and terminating inwardly inan oil inlet area having said oil inlet, the total of said pad surfacearea being greater than said oil inlet area for each pad, said isolatedpad surfaces with said pressurized oil films thereon against said slidessupporting said ram carriage on said main frame during said horizontallyreciprocal movement.
 9. Metal forming apparatus as defined in claim 1 inwhich said ram is mounted on a ram carriage and is generallyhorizontally reciprocal on said main frame movable in said forward andrearward strokes by forward and rearward strokes of said ram carriage;in which hydrostatic-type pressurized oil film bearing assembliesinclude ram carriage and main frame oil bearing parts supporting saidram carriage on said main frame during said ram and ram carriagegenerally horizontal reciprocal movements, said ram carriage oil bearingparts being secured movable with said ram carriage and moving relativeto said main frame oil bearing parts secured stationary on said mainframe, said main frame oil bearing parts including slides havingupwardly and downwardly facing generally horizontal surfaces thereon andoppositely transversely facing generally vertical surfaces thereon allparallel to said ram movements, said ram carriage oil bearing partsincluding sets of vertically spaced pads transversely horizontallyspaced at opposite sides of a longitudinal axis of said ram, each ofsaid pads having a generally horizontal flat surface thereon parallel tosaid ram movements, one of said pads of each of said vertically spacedsets being positioned with one pad horizontal surfaces downwardly facingsaid slide upwardly facing horizontal surfaces and the other padhorizontal surfaces upwardly facing said slide downwardly facinghorizontal surfaces with a slide spaced vertically therebetween,pressurized oil inlets opening through each of said pad horizontalsurfaces and connected to pressurized oil supply means distributingconstantly flowing and pressurized, thickened oil films through saidinlet over and between said pad and slide facing horizontal surfacesmaintaining said pad surfaces spaced from said slide surfaces andpressure oil film supporting said ram carriage by both vertically upwardand downward forces during said ram and ram carriage reciprocalmovements to thereby support said ram horizontally movable on said mainframe; in which said ram carriage oil bearing parts include at least oneset of pads having generally vertical flat surfaces thereon parallel tosaid ram movements and in the same general longitudinal location of saidvertically spaced pads, each of said vertical surface pads beingpositioned with one pad vertical surfaces transversely facing acorresponding of said slide vertical surfaces, pressurized oil inletsopening through each of said pad vertical surfaces and connected topressurized oil supply means distributing constantly flowing andpressurized, thickened oil films through said inlet over and betweensaid pad and slide facing vertical surfaces maintaining said padsurfaces spaced transversely from said slide surfaces and pressure oilfilm supporting said ram carriage transversely during said ramreciprocal movements and in which each of said ram carriage pads iscomprised of a raised flat surface area constituting said pad surfacehorizontally isolated from all surrounding surfaces, said each padsurface surrounding and terminating inwardly in an oil inlet area havingsaid oil inlet, the total of said pad surface area being greater thansaid oil inlet area for each pad, said isolated pad surfaces with saidpressurized oil films thereon against said slides supporting said ramcarriage on said main frame during said horizontally reciprocalmovement.
 10. Metal forming apparatus as defined in claim 1 in whichsaid ram is mounted on a ram carriage projecting generally horizontallyforwardly therefrom and is generally horizontally reciprocal on saidmain frame in said forward and rearward strokes by forward and rearwardgenerally horizontal movements of said ram carriage; in whichhydrostatic-type pressurized oil film bearing assemblies including ramcarriage and main frame oil bearing parts supporting said ram carriageon said main frame during said ram and ram carriage generally horizontalreciprocal movements, said ram carriage oil bearing parts being securedmovable with said ram carriage and moving relative to said main frameoil bearing parts secured stationary on said main frame, one of said ramcarriage and main frame oil bearing parts including slides havingsurfaces thereon parallel to said ram movements, the other of said ramcarriage and main frame oil bearing parts including spaced pads havingflat surfaces thereon parallel to said ram movements, said pads beingpositioned with said pad surfaces at all times at least partiallygenerally vertically facing and adjacent to said slide surfaces,pressurized oil inlets opening through each of said Pad surfaces andconnected to pressurized oil supply means distributing constantlyflowing and pressurized, thickened oil films through said inlets overand between said pad and slide surfaces maintaining said pad surfacesspaced from said slide surfaces and pressure oil film supporting saidram carriage during said ram and ram carriage reciprocal movements, atleast certain of said ram carriage bearing parts being positionedexerting vertical force components through said oil films actinggenerally vertically downwardly against opposed upward force componentsof facing of said main frame oil bearing parts providing support atleast by vertical force components of said ram carriage on said mainframe, each of said pads being comprised of a raised flat surface areaconstituting said pad surface horizontally isolated from all surroundingsurfaces, said each pad surface surrounding and terminating inwardly inan oil inlet area having said oil inlet, the total of said pad surfacearea being greater than said oil inlet area for each pad, said isolatedpad surfaces with said pressurized oil films thereon against said slidessupporting said ram carriage on said main frame; and in which ahydrostatic-type pressure oil film bearing sleeve is secured stationaryon said main frame at all times spaced forwardly of said ram carriageand telescoping part of said ram during said reciprocal movements ofsaid ram, said bearing sleeve having a plurality of pressurized oilinlets opening through an inner surface of said sleeve against aperipheral surface of said ram spaced about said ram peripheral surface,pressurized oil supply means connected to said bearing sleeve oil inletsdistributing a constantly flowing and pressurized, thickened oil filmthrough said inlets over and between said sleeve inner surface and saidram peripheral surface maintaining said sleeve and ram surfaces spacedapart by said constantly flowing and pressurized oil film for pressureoil film supporting said ram part during said ram reciprocal movementsso that the combination of said ram carriage and said bearing sleeve inspaced relationship support said ram in such movements.
 11. Metalforming apparatus as defined in claim 1 in which said ram is mounted ona ram carriage projecting generally horizontally forwardly therefrom andis generally horizontally reciprocal on said main frame in said forwardand rearward strokes by forward and rearward generally horizontalstrokes of said ram carriage; in which hydrostatic-type pressurized oilfilm bearing assemblies including ram carriage and main frame oilbearing parts supporting said ram carriage on said main frame duringsaid ram and ram carriage generally horizontal reciprocal movements,said ram carriage oil bearing parts being secured movable with said ramcarriage and moving relative to said main frame oil bearing partssecured stationary on said main frame, one of said ram carriage and mainframe oil bearing parts including slides having generally horizontalsurfaces and transversely spaced generally vertical surfaces thereonparallel to said ram movements, the other of said ram carriage and mainframe oil bearing parts including spaced horizontal pads havinggenerally horizontal flat surfaces thereon and transversely spacedvertical pads having generally vertical flat surfaces thereon parallelto said ram movements, said horizontal pads being positioned with saidpad horizontal surfaces at all times generally vertically facing andadjacent said slide horizontal surfaces, said vertical pads beingpositioned with said pad vertical surfaces at all times generallyvertically facing and adjacent corresponding of said slide verticalsurfaces, pressurized oil inlets openings through each of saidhorizontal and vertical pad horizontal and vertical surfaces andconnected to pressurized oil supply means distributing constantlyflowing and pressurized, thickened oil films through said inlets overand between said pad and slide horizontal and vertical surfacesmaintaining sAid pad surfaces spaced from slide surfaces and pressureoil film supporting said ram carriage during said ram and ram carriagereciprocal movements, at least certain of said ram carriage oil bearingparts being positioned acting generally vertically downwardly againstcorrespondingly facing and upwardly acting of said main frame oilbearing parts through said facing horizontal surfaces and saidpressurized oil film therebetween providing said horizontal support ofsaid ram carriage on said main frame, said ram carriage and main frameoil bearing parts having said facing vertical surfaces acting generallyhorizontally between said ram carriage and main frame with saidpressurized oil film therebetween providing transverse support of saidram carriage on said main frame, each of said pads being comprised of araised flat surface area constituting said pad surface horizontallyisolated from all surrounding surfaces, said each pad surfacesurrounding and terminating inwardly in an oil inlet area having saidoil inlet, the total of said pad surfaces area being greater than saidoil inlet area for each pad, said isolated pad surfaces with saidpressurized oil films thereon against said slides supporting said ramcarriage on said main frame during said horizontal reciprocal movement;and in which a hydrostatic-type pressure oil film bearing sleeve issecured stationary on said main frame at all times spaced forwardly ofsaid ram carriage and telescoping parts of said ram during saidreciprocal movements of said ram, said bearing sleeve having a pluralityof pressurized oil inlets opening through an inner surface of saidsleeve against a peripheral surface of said ram spaced about said ramperipheral surface, pressurized oil supply means connected to saidbearing sleeve oil inlets distributing a constantly flowing andpressurized, thickened oil film through said inlets over and betweensaid sleeve inner surface and said ram peripheral surface maintainingsaid sleeve and ram surfaces spaced apart by said constantly flowing andpressurized oil film for pressure oil film supporting said ram partsduring said ram reciprocal movement so that the combination of said ramcarriage and said bearing sleeve in spaced relationship support said ramin such movements.
 12. In metal forming apparatus of the type having amain frame mounting a longitudinally reciprocal ram on a ram carriageboth movable in generally horizontal forward and rearward strokes withforward and rearward reversals between said strokes, said ram beingadapted for having a metal part positioned to be engaged thereby andformed at least during a part of said forward stroke; the improvementscomprising: hydrostatic-type pressurized oil film bearing assembliesincluding ram carriage and main frame oil bearing parts supporting saidram carriage on said main frame during said ram and ram carriagegenerally horizontal reciprocal movements, said ram carriage oil bearingparts being secured movable with said ram carriage and moving relativeto said main frame oil bearing parts secured stationary on said mainframe; one of said ram carriage and main frame oil bearing partsincluding slides having surfaces thereon parallel to said ram movements;the other of said ram carriage and main frame oil bearing partsincluding spaced pads having flat surfaces thereon parallel to said rammovements, said pads being positioned with said pad surfaces at alltimes at least partially generally vertically facing and adjacent saidslide surfaces, pressurized oil inlets opening through each of said padsurfaces and connected to pressurized oil supply means distributingconstantly flowing and pressurized, thickened oil films through saidinlets over and between said pad and slide surfaces maintaining said padsurfaces spaced from said slide surfaces and pressure oil filmsupporting said ram carriage during said ram and ram carriage reciprocalmovements; at least certain of said ram carriage oil bearing parts beingpositioned exerting vertical force components through said oil filmsacting generally vertically downwardly against upward force componentsof facing of said main frame oil bearing parts providing at least byvertical force components horizontal support of said ram carriagemovable on said main frame; and each of said spaced pads being comprisedof a raised flat surface area constituting said pad surface horizontallyisolated from all surrounding surfaces, said each pad surfacesurrounding and terminating inwardly in an oil inlet area having saidoil inlet, the total of said pad surface area being greater than saidoil inlet area for each pad, said isolated pad surfaces with saidpressurized oil films thereon against said slides supporting said ramcarriage on said main frame during said horizontally reciprocalmovement.
 13. Metal forming apparatus as defined in claim 12 in whichsaid one of said ram carriage and main frame oil bearing parts includesaid slides having a least partially generally upwardly and downwardlyfacing surfaces thereon parallel to said ram movements; and in whichsaid other of said ram carriage and main frame oil bearing parts includehorizontally spaced sets of vertically spaced pads, each of said sets ofvertically spaced pads having one of said pad flat surfaces facing atleast partially generally upwardly and the other of said pad flatsurfaces facing at least partially generally downwardly corresponding tosaid slide surfaces at all times facing said corresponding of said slidesurfaces.
 14. Metal forming apparatus as defined in claim 12 in whichsaid other of said ram carriage and main frame oil bearing parts includeat least certain of said pads being transversely spaced sets oflongitudinally spaced pads and forming at least a part of said at leastcertain ram carriage oil bearing parts and said corresponding main frameoil bearing parts.
 15. Metal forming apparatus as defined in claim 12 inwhich said one of said ram carriage and main frame oil bearing partsinclude said slides having at least partially generally upwardly facingsurfaces and at least partially generally downwardly facing surfacesthereon parallel to said ram movements; and in which said other of saidram carriage and main frame oil bearing parts include at least partiallygenerally upwardly and downwardly acting pads at spaced longitudinallocations and at spaced transverse locations all acting againstcorresponding upwardly and downwardly facing oil bearing part slidesurfaces providing through said facing surfaces and said pressurized oilfilm therebetween upward and downward horizontal force component supportof said ram carriage in said longitudinal reciprocal movements of saidram and ram carriage on said main frame.
 16. Metal forming apparatus asdefined in claim 12 in which said one of said ram carriage and mainframe oil bearing parts include said slides having at least partiallygenerally transversely facing surfaces thereon facing transverselyopposite and extending parallel to said ram movements; and in which saidother of said ram carriage and main frame oil bearing parts include saidpads having generally horizontally spaced corresponding at leastpartially transversely facing surfaces thereon parallel to said rammovements and facing said surfaces on said oil bearing part slides, saidpressurized oil inlets opening through each of said pad surfaces andconnected to pressurized oil supply means distributing a constantlyflowing and pressurized, thickened oil film through said inlets over andbetween said pad and slide surfaces maintaining said pad surfaces spacedfrom said slide surfaces and providing force components alsotransversely pressure oil film supporting said ram carriage during saidram and ram carriage longitudinal reciprocal movements.
 17. Metalforming apparatus as defined in claim 12 in which said one of said ramcarriage and main frame oil bearing parts include slides having upwardlyand downwardly facing generally horizontal surfaces thereon andgenerally veRtical surfaces thereon facing transversely oppositely, allof said horizontal and vertical surfaces extending parallel to said rammovements; in which said other of said ram carriage and main frame oilbearing parts include horizontally spaced sets of vertically spacedpads, each of said sets of vertically spaced pads having one of said padhorizontal surfaces facing upwardly and the other of said pad horizontalsurfaces facing downwardly at all times generally facing correspondingof said slide horizontal surfaces, said pressurized oil inlets openingthrough each of said pad horizontal surfaces distributing saidconstantly flowing and pressurized, thickened oil films over and betweensaid pad and slide horizontal surfaces maintaining said pad surfacesspaced from said slide surfaces and pressure oil film supporting saidram carriage both upwardly and downwardly during said ram and ramcarriage longitudinal reciprocal movements; and in which said other ofsaid ram carriage and main frame oil bearing parts include pads havinggenerally horizontally spaced vertical surfaces thereon parallel to saidram movements and facing corresponding of said vertical surfaces on saidoil bearing part slides, pressurized oil inlets opening through each ofsaid pad vertical surfaces and connected to pressurized oil supply meansdistributing a constantly flowing and pressurized, thickened oil filmthrough said inlets over and between said pad and slide verticalsurfaces maintaining said pad surfaces spaced transversely from saidslide surfaces and transversely pressure oil film supporting said ramcarriage during said ram and ram carriage longitudinal reciprocalmovements.
 18. Metal forming apparatus as defined in claim 12 in whichsaid one of said ram carriage and main frame oil bearing parts includesaid slides having upwardly facing generally horizontal surfaces anddownwardly facing generally horizontal surfaces thereon and generallyvertical surfaces thereon facing transversely oppositely, all of saidhorizontal and vertical surfaces extending parallel to said rammovements; in which said other of said ram carriage and main frame oilbearing parts include upwardly and downwardly acting pads at spacedlongitudinal locations and at spaced transverse locations all actingagainst corresponding upwardly and downwardly facing oil bearing partslide surfaces providing through said facing horizontal surfaces andsaid pressurized oil film therebetween upward and downward horizontalsupport of said ram carriage in said longitudinal reciprocal movementson said main frame; and in which said other of said ram carriage andmain frame oil bearing parts include longitudinally spaced sets of padseach having vertical surfaces thereon parallel to said ram movement,said pad vertical surfaces of each set facing transversely oppositelyand facing corresponding of said vertical surfaces on said oil bearingpart slides, pressurized oil inlets opening through each of said padvertical surfaces and connected to pressurized oil supply meansdistributing a constantly flowing and pressurized, thickened oil filmthrough said inlet over and between said pad and slide vertical surfacesmaintaining said pad surfaces spaced transversely from said slidesurfaces and transversely pressure oil film supporting said ram carriageduring said ram and ram carriage longitudinal reciprocal movements. 19.Metal forming apparatus as defined in claim 12 in which said ramprojects forwardly from said ram carriage; and in which ahydrostatic-type pressurized oil film bearing sleeve is securedstationary on said main frame at all times spaced forwardly of said ramcarriage and telescoping parts of said ram during said reciprocalmovements of said ram and ram carriage, said bearing sleeve having aplurality of pressurized oil inlets opening through an inner surface ofsaid sleeve against a peripheral surface of said ram spaced about saidram peripheral surface, pressurized oil supply means connected to saidbearing sleeve oil inLets distributing a constantly flowing andpressurized, thickened oil film through said inlets over and betweensaid sleeve inner surface and said ram peripheral surface maintainingsaid sleeve and ram surfaces spaced apart by said constantly flowing andpressurized oil film for pressure oil film supporting said ram partsduring said ram and ram carriage reciprocal movements so that thecombination of said ram carriage and said bearing sleeve in spacedrelationship support said ram in such movements.
 20. Metal formingapparatus as defined in claim 12 in which said ram projects forwardlyfrom said ram carriage; in which said one of said ram carriage and mainframe oil bearing parts include slides having upwardly and downwardlyfacing generally horizontal surfaces thereon and generally verticalsurfaces thereon facing transversely oppositely, all of said horizontaland vertical surfaces extending parallel to said ram movements; in whichsaid other of said ram carriage and main frame oil bearing parts includehorizontally spaced sets of vertically spaced pads, each of said sets ofvertically spaced pads having one of said pad horizontal surfaces facingupwardly and the other of said pad horizontal surfaces facing downwardlyat all times generally facing corresponding of said slide horizontalsurfaces, said pressurized oil inlets opening through each of said padhorizontal surfaces distributing said constantly flowing andpressurized, thickened oil films over and between said pad and slidehorizontal surfaces maintaining said pad surfaces spaced from said slidesurfaces and pressure oil film supporting said ram carriage bothupwardly and downwardly during said ram and ram carriage longitudinalreciprocal movements; in which said other of said ram carriage and mainframe oil bearing parts include pads having generally horizontallyspaced vertical surfaces thereon parallel to said ram movements andfacing corresponding of said vertical surfaces on said oil bearing partslides, pressurized oil inlets opening through each of said pad verticalsurfaces and connected to pressurized oil supply means distributing aconstantly flowing and pressurized, thickened oil film through saidinlets over and between said pad and slide vertical surfaces maintainingsaid pad surfaces spaced transversely from said slide surfaces andtransversely pressure oil film supporting said ram carriage during saidram and ram carriage longitudinal reciprocal movements; in which all ofsaid pads of said other of said ram carriage and main frame oil bearingparts are similarly formed and isolated; and in which a hydrostatic-typepressurized oil film bearing sleeve is secured stationary on said mainframe at all times spaced forwardly of said ram carriage and telescopingparts of said ram during said reciprocal movements of said ram and ramcarriage, said bearing sleeve having a plurality of pressurized oilinlets opening through an inner surface of said sleeve against aperipheral surface of said ram spaced about said ram spaced about saidram peripheral surface, pressurized oil supply means connected to saidbearing sleeve oil inlets distributing a constantly flowing andpressurized, thickened oil film through said inlets over and betweensaid sleeve inner surface and said ram peripheral surface maintainingsaid sleeve and ram surfaces spaced apart by said constantly flowing andpressurized oil film for pressure oil film supporting said ram partsduring said ram and ram carriage reciprocal movements so that thecombination of said ram carriage and said bearing sleeve in spacedrelationship support said ram in such movements.